US20150260302A1 - Dual/variable gain oil pump control valve - Google Patents
Dual/variable gain oil pump control valve Download PDFInfo
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- US20150260302A1 US20150260302A1 US14/206,442 US201414206442A US2015260302A1 US 20150260302 A1 US20150260302 A1 US 20150260302A1 US 201414206442 A US201414206442 A US 201414206442A US 2015260302 A1 US2015260302 A1 US 2015260302A1
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- control valve
- feedback
- solenoid
- fluid control
- fluid
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- 230000009977 dual effect Effects 0.000 title description 21
- 239000012530 fluid Substances 0.000 claims abstract description 97
- 230000004044 response Effects 0.000 claims abstract description 9
- 238000006073 displacement reaction Methods 0.000 claims abstract description 4
- 230000007246 mechanism Effects 0.000 claims description 15
- 230000008859 change Effects 0.000 claims description 3
- 239000000356 contaminant Substances 0.000 description 5
- 238000011109 contamination Methods 0.000 description 3
- RYGMFSIKBFXOCR-UHFFFAOYSA-N Copper Chemical compound [Cu] RYGMFSIKBFXOCR-UHFFFAOYSA-N 0.000 description 1
- 230000008901 benefit Effects 0.000 description 1
- 230000001276 controlling effect Effects 0.000 description 1
- 229910052802 copper Inorganic materials 0.000 description 1
- 239000010949 copper Substances 0.000 description 1
- 230000002596 correlated effect Effects 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
Images
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K31/00—Actuating devices; Operating means; Releasing devices
- F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
- F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
- F16K31/0603—Multiple-way valves
- F16K31/061—Sliding valves
- F16K31/0613—Sliding valves with cylindrical slides
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
- F15B13/042—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure
- F15B13/043—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure with electrically-controlled pilot valves
- F15B13/0433—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure with electrically-controlled pilot valves the pilot valves being pressure control valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K11/00—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves
- F16K11/02—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit
- F16K11/06—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements
- F16K11/065—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with linearly sliding closure members
- F16K11/07—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with linearly sliding closure members with cylindrical slides
- F16K11/0716—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with linearly sliding closure members with cylindrical slides with fluid passages through the valve member
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K15/00—Check valves
- F16K15/18—Check valves with actuating mechanism; Combined check valves and actuated valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K15/00—Check valves
- F16K15/18—Check valves with actuating mechanism; Combined check valves and actuated valves
- F16K15/182—Check valves with actuating mechanism; Combined check valves and actuated valves with actuating mechanism
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K31/00—Actuating devices; Operating means; Releasing devices
- F16K31/12—Actuating devices; Operating means; Releasing devices actuated by fluid
- F16K31/42—Actuating devices; Operating means; Releasing devices actuated by fluid by means of electrically-actuated members in the supply or discharge conduits of the fluid motor
- F16K31/423—Actuating devices; Operating means; Releasing devices actuated by fluid by means of electrically-actuated members in the supply or discharge conduits of the fluid motor the actuated members consisting of multiple way valves
- F16K31/426—Actuating devices; Operating means; Releasing devices actuated by fluid by means of electrically-actuated members in the supply or discharge conduits of the fluid motor the actuated members consisting of multiple way valves the actuated valves being cylindrical sliding valves
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T137/00—Fluid handling
- Y10T137/8593—Systems
- Y10T137/86493—Multi-way valve unit
- Y10T137/86574—Supply and exhaust
- Y10T137/8667—Reciprocating valve
- Y10T137/86694—Piston valve
- Y10T137/8671—With annular passage [e.g., spool]
Definitions
- the present invention relates to an electromagnetic solenoid actuator having an armature mechanism that drives a fluid control element.
- Direct acting solenoid actuators are often used to control fluid pressure in a variety of systems, including clutch mechanisms and other devices in an automobile.
- Direct acting solenoid actuators employ an armature mechanism that drives a fluid control element, such as a spool, a spring-biased four-way proportional flow control valve, a poppet valve, and the like in various hydraulic control applications.
- the armature is connected to, and drives, a push pin that engages the fluid control element to this end.
- the fluid control element may comprise a spool surrounded by a valve body.
- the spool may be connected to the push pin such that any motion of the armature results in motion of the spool.
- the position of the spool, and the resulting fluid pressure, are directly dependent on the position of the armature.
- the coil therefore, must produce a sufficiently strong magnetic field to move the spool under any pressure condition. To achieve this, the coil may require many loops, dictating the size of the apparatus and requiring a large quantity of copper wiring.
- a solenoid fluid control valve for controlling a variable displacement pump.
- the solenoid fluid control valve comprises a fixed solenoid component, a movable armature component, a fixed nozzle body, a movable spool within the fixed nozzle body, and a valve member.
- the valve member regulates fluid pressure in a first and second feedback chamber. Fluid in the second feedback chamber establishes a second feedback pressure that acts on the movable spool with a motive feedback force in a first axial direction.
- the movable spool moves in the first axial direction in response to the motive feedback force.
- FIG. 1 shows a direct acting solenoid fluid control valve
- FIG. 2 shows a dual gain solenoid fluid control valve in a de-energized state
- FIG. 3 shows the dual gain solenoid fluid control valve in an energized state
- FIG. 4 illustrates a cross-section of the dual gain solenoid fluid control valve shown in FIG. 3 ;
- FIG. 5 shows an exhaust path for fluid in the outer feedback chamber
- FIG. 6 shows a continuation of the exhaust path in a cross-section of the dual gain solenoid fluid control valve shown in FIG. 5 ;
- FIG. 7 shows a second embodiment of the dual gain solenoid fluid control valve in a de-energized state
- FIG. 8 shows the second embodiment of the dual gain solenoid fluid control valve in an energized state.
- FIG. 1 A direct acting solenoid fluid control valve is shown in FIG. 1 .
- the direct acting solenoid fluid control valve 100 comprises a housing 102 containing a bobbin 104 , and a coil of wire 106 wound on the bobbin 104 and connected to electrical terminals 108 .
- An armature 110 moves in response to a current through the coil 106 .
- the reduced diameter end of the armature 110 is fixed to the adjacent end of a spool 112 .
- a nozzle body 114 includes a supply port 116 ; a control port 118 ; and an exhaust port 120 .
- the spool 112 is moved in response to movement of the armature 110 to regulate pressure or flow at the control port 118 .
- the spool 112 and thus the armature 110 , is biased by a spring mechanism 122 .
- the control port 118 is open to the supply port 116 , as shown in FIG. 1 .
- Supplying power to the coil 106 causes the armature 110 to move in the direction of the spring mechanism 122 , displacing the spool 112 and connecting the control port 118 to the exhaust port 120 , thereby reducing the pressure at the control port.
- the pressure at the control port 118 therefore directly depends upon the position of the spool 112 , and accordingly, the position of the armature 110 .
- the force on the armature 110 induced by the current through the coil 106 must be sufficiently strong to displace the spool and compress the spring mechanism 122 . For a large spool, this may require many turns of the coil 106 , contributing to the device's size, weight, and cost.
- the dual gain solenoid fluid control valve 200 comprises a housing 202 containing a bobbin 204 , and a coil of wire 206 wound on the bobbin 204 and connected to electrical terminals 208 .
- An armature 210 moves in response to a current through the coil 206 .
- the armature may be fixed to an actuator pin 212 .
- a valve member 214 is located within a piston 216 , and seals an opening 218 in the piston 216 when the coil 206 is in the de-energized state. This state is shown in FIG. 2 .
- An end of the spool 220 fits into an end of the piston 216 opposite the opening 218 .
- a nozzle body 222 surrounds the spool 220 and the piston 216 .
- the nozzle body 222 includes supply port 224 defined between O-ring seals 226 and 228 and protected by filter 230 ; control port 232 defined between O-ring seals 228 and 234 and protected by filter 236 ; and exhaust port 238 .
- the spool 220 is moved to regulate pressure at the control port 232 .
- a calibration cap 240 fits into the end of the nozzle body 222 opposite the armature 210 . The calibration cap 240 may be tightened or loosened to change the force of the spring mechanism 242 on the spool 220 .
- the spool 220 includes a radial spool bore 244 and longitudinal spool bore 246 that connect the supply port 224 to the piston chamber 248 .
- the combined space in the longitudinal spool bore 246 and piston chamber 248 is referred to herein as the inner feedback chamber 246 , 248 .
- the first feedback force depends on the supply pressure and the axial fluid contracting area of the inner feedback chamber 246 , 248 .
- the supply port 224 communicates to the control port 232 , as shown in FIG. 2 .
- FIG. 3 shows the solenoid fluid control valve 300 in the energized state, wherein like numbers in as in FIG. 2 correspond to like elements.
- the coil 306 When the coil 306 is energized, the armature 310 and pushpin 312 move axially, displacing the valve member 314 from the opening 318 in the piston 316 .
- Fluid in the inner feedback chamber 346 , 348 flows through the opening 318 and into the outer feedback chamber 350 . Because the outer feedback chamber 350 increases considerably the contacting area that the fluid acts on in addition to the inner feedback area 346 , 348 , the fluid now exerts a much larger force on the spool 320 .
- control port 332 communicates to the exhaust port 338 , reducing the pressure at the control port (i.e., control pressure).
- FIG. 4 shows a cross-sectional view of the dual gain solenoid fluid control valve. The view is taken from the position of the dashed line 352 in FIG. 3 , although the valve member 314 is not shown.
- the nozzle body 400 surrounds the cylindrical piston wall 402 , which is fixed to the rectangular piston base 404 .
- a hole 406 in the piston base 404 is sufficiently wide to permit fluid to exit the inner feedback area while the pushpin 408 extends through the hole 406 .
- the fluid passes under the piston base 404 and through the opening 410 between the rectangular piston base 404 and the cylindrical nozzle body 400 , into the outer feedback chamber.
- FIG. 6 shows a cross-sectional view of the solenoid fluid control valve taken at the dashed line 514 in FIG. 5 .
- fluid travels from an inner to an outer area between the washer and the bobbin and exits through an exhaust port 600 .
- the departure of fluid from the outer feedback chamber reduces the pressure in that area, allowing the spool to return to its initial position.
- the dual gain solenoid fluid control valve 300 requires less force from the coil 306 than the direct acting solenoid fluid control valve of FIG. 1 requires.
- the force from the coil 306 is only required to displace the valve member 314 from the opening in 318 in the piston 316 .
- fluid in the inner feedback chamber 346 , 348 and outer feedback chamber 350 provides the force that displaces the spool 220 and compresses the spring mechanism 242 .
- the force from the coil 106 in the direct acting solenoid fluid control valve 100 shown in FIG. 1 must be sufficient to displace the entire spool 112 and compress the spring mechanism 122 .
- This greater force requires more turns of the coil 106 , resulting in a larger, more expensive device.
- the dual gain solenoid fluid control valve utilizes the fluid pressure in the inner and outer feedback chambers to move the spool, thereby requiring fewer turns of the coil, and therefore allowing for a reduction in the device's size and cost.
- the dual gain solenoid fluid control valve has a further advantage of improved robustness to contamination.
- Contamination can greatly affect the performance of a solenoid fluid control valve, as small contaminants in the fluid flowing through the valve may become lodged between moving and stationary elements, obstructing the smooth motion of the armature and spool. This obstruction may lead to hysteresis, as well as to variable responses to a given command current. Accordingly, the presence of contaminants may quickly degrade the solenoid fluid control valve's performance and reliability.
- the first and second feedback chambers of the dual gain solenoid fluid control valve allow fluid to travel through wide passages within the device.
- the fluid may carry contaminants, but the wide chambers allow the valve to function without being inhibited by the contaminants. This increased robustness improves the reliability of the device, allowing for look-up tables to be created relating a current in the coil for a resulting control pressure.
- the lifetime of the device may also be extended as wear due to contaminants is minimized.
- a pulse width modulated (PWM) signal may be used to provide variations in the control pressure.
- the spring cap may be tightened or loosened to adjust the position of the spool in the energized and de-energized states. Once the two positions have been determined, the duty cycle of the PWM signal may determine how much time the solenoid spends in each state, thereby creating a variable control pressure.
- FIGS. 7 and 8 Another embodiment of the dual gain solenoid fluid control valve is shown in FIGS. 7 and 8 , wherein like numbers as in FIGS. 2 and 3 indicate like elements.
- the dual gain solenoid fluid control valve 700 is in the de-energized state.
- the radial spool bore 744 is moved to a tapered region of the spool 720 .
- the radial spool bore 744 is open to the supply port 724 and the control port 732 .
- the dual feedback from the inner feedback chamber 846 , 848 and outer feedback chambers 850 moves the spool such that the radial spool bore 844 is open to the supply port 832 and the exhaust port 838 .
- the calibration cap 840 may be tightened or loosened to adjust the force of the spring mechanism 842 on the spool 820 . This force in turn determines the position of the spool 820 when the coil 806 is in the de-energized and energized states. Accordingly, the spool position in the de-energized and energized states may not exactly correspond to the positions shown in FIGS. 7 and 8 .
- the inner and outer feedback pressure now depends on both the supply and control pressures, and not just the supply pressure.
- the placement of the radial spool bore 844 allows the device to be configured such that a small control pressure remains even when the coil 806 is energized, and the control pressure it at a minimum. Having a non-zero minimum control pressure allows the valve to be more responsive to a change in the current through the coil. This improved response allows the valve to be more accurately controlled by a PWM signal.
- the dual gain solenoid fluid control valve may be used to control a variable displacement pump, wherein the valve's control pressure regulates the flow of fluid through the pump.
- the pump requires that the valve's response to a given command current be accurate and reliable, so that the command current may be correlated with a flow through the pump.
- the dual gain solenoid fluid control valve provides a reliable control pressure that is robust to contamination and responsive to small changes in the command current.
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- Magnetically Actuated Valves (AREA)
Abstract
Description
- The present invention relates to an electromagnetic solenoid actuator having an armature mechanism that drives a fluid control element.
- Direct acting solenoid actuators are often used to control fluid pressure in a variety of systems, including clutch mechanisms and other devices in an automobile. Direct acting solenoid actuators employ an armature mechanism that drives a fluid control element, such as a spool, a spring-biased four-way proportional flow control valve, a poppet valve, and the like in various hydraulic control applications. Typically, the armature is connected to, and drives, a push pin that engages the fluid control element to this end.
- The fluid control element may comprise a spool surrounded by a valve body. The spool may be connected to the push pin such that any motion of the armature results in motion of the spool. The position of the spool, and the resulting fluid pressure, are directly dependent on the position of the armature. The coil, therefore, must produce a sufficiently strong magnetic field to move the spool under any pressure condition. To achieve this, the coil may require many loops, dictating the size of the apparatus and requiring a large quantity of copper wiring.
- A solenoid fluid control valve is disclosed for controlling a variable displacement pump. The solenoid fluid control valve comprises a fixed solenoid component, a movable armature component, a fixed nozzle body, a movable spool within the fixed nozzle body, and a valve member. The valve member regulates fluid pressure in a first and second feedback chamber. Fluid in the second feedback chamber establishes a second feedback pressure that acts on the movable spool with a motive feedback force in a first axial direction. The movable spool moves in the first axial direction in response to the motive feedback force.
-
FIG. 1 shows a direct acting solenoid fluid control valve; -
FIG. 2 shows a dual gain solenoid fluid control valve in a de-energized state; -
FIG. 3 shows the dual gain solenoid fluid control valve in an energized state; -
FIG. 4 illustrates a cross-section of the dual gain solenoid fluid control valve shown inFIG. 3 ; -
FIG. 5 shows an exhaust path for fluid in the outer feedback chamber; -
FIG. 6 shows a continuation of the exhaust path in a cross-section of the dual gain solenoid fluid control valve shown inFIG. 5 ; -
FIG. 7 shows a second embodiment of the dual gain solenoid fluid control valve in a de-energized state; and -
FIG. 8 shows the second embodiment of the dual gain solenoid fluid control valve in an energized state. - A direct acting solenoid fluid control valve is shown in
FIG. 1 . The direct acting solenoidfluid control valve 100 comprises ahousing 102 containing abobbin 104, and a coil ofwire 106 wound on thebobbin 104 and connected toelectrical terminals 108. Anarmature 110 moves in response to a current through thecoil 106. The reduced diameter end of thearmature 110 is fixed to the adjacent end of aspool 112. Anozzle body 114 includes asupply port 116; a control port 118; and anexhaust port 120. Thespool 112 is moved in response to movement of thearmature 110 to regulate pressure or flow at the control port 118. Thespool 112, and thus thearmature 110, is biased by aspring mechanism 122. - For an initially high pressure solenoid fluid control valve, the control port 118 is open to the
supply port 116, as shown inFIG. 1 . Supplying power to thecoil 106 causes thearmature 110 to move in the direction of thespring mechanism 122, displacing thespool 112 and connecting the control port 118 to theexhaust port 120, thereby reducing the pressure at the control port. The pressure at the control port 118 therefore directly depends upon the position of thespool 112, and accordingly, the position of thearmature 110. The force on thearmature 110 induced by the current through thecoil 106 must be sufficiently strong to displace the spool and compress thespring mechanism 122. For a large spool, this may require many turns of thecoil 106, contributing to the device's size, weight, and cost. - A dual gain solenoid fluid control valve is shown in
FIG. 2 . The dual gain solenoidfluid control valve 200 comprises ahousing 202 containing abobbin 204, and a coil ofwire 206 wound on thebobbin 204 and connected toelectrical terminals 208. Anarmature 210 moves in response to a current through thecoil 206. The armature may be fixed to anactuator pin 212. - A
valve member 214 is located within apiston 216, and seals an opening 218 in thepiston 216 when thecoil 206 is in the de-energized state. This state is shown inFIG. 2 . An end of thespool 220 fits into an end of thepiston 216 opposite the opening 218. Anozzle body 222 surrounds thespool 220 and thepiston 216. Thenozzle body 222 includessupply port 224 defined between O-ring seals filter 230;control port 232 defined between O-ring seals filter 236; andexhaust port 238. Thespool 220 is moved to regulate pressure at thecontrol port 232. Acalibration cap 240 fits into the end of thenozzle body 222 opposite thearmature 210. Thecalibration cap 240 may be tightened or loosened to change the force of thespring mechanism 242 on thespool 220. - In one embodiment of the invention, the
spool 220 includes a radial spool bore 244 and longitudinal spool bore 246 that connect thesupply port 224 to thepiston chamber 248. The combined space in the longitudinal spool bore 246 andpiston chamber 248 is referred to herein as theinner feedback chamber coil 206 is in the de-energized state, fluid from thesupply port 224 fills theinner feedback chamber spool 220 that balances the force of thespring mechanism 242. The first feedback force depends on the supply pressure and the axial fluid contracting area of theinner feedback chamber supply port 224 communicates to thecontrol port 232, as shown inFIG. 2 . -
FIG. 3 shows the solenoidfluid control valve 300 in the energized state, wherein like numbers in as inFIG. 2 correspond to like elements. When thecoil 306 is energized, thearmature 310 andpushpin 312 move axially, displacing thevalve member 314 from theopening 318 in thepiston 316. Fluid in theinner feedback chamber opening 318 and into theouter feedback chamber 350. Because theouter feedback chamber 350 increases considerably the contacting area that the fluid acts on in addition to theinner feedback area spool 320. This force now exceeds the opposing force of thespring mechanism 342, and thespool 320 moves toward thespring mechanism 342, into the position shown inFIG. 3 . In this state, thecontrol port 332 communicates to theexhaust port 338, reducing the pressure at the control port (i.e., control pressure). -
FIG. 4 shows a cross-sectional view of the dual gain solenoid fluid control valve. The view is taken from the position of thedashed line 352 inFIG. 3 , although thevalve member 314 is not shown. Referring toFIG. 4 , thenozzle body 400 surrounds thecylindrical piston wall 402, which is fixed to therectangular piston base 404. Ahole 406 in thepiston base 404 is sufficiently wide to permit fluid to exit the inner feedback area while thepushpin 408 extends through thehole 406. The fluid passes under thepiston base 404 and through theopening 410 between therectangular piston base 404 and thecylindrical nozzle body 400, into the outer feedback chamber. - Referring now to
FIG. 5 , when thecoil 500 is returned to its de-energized state, fluid in the inner feedback chamber 516 andouter feedback chamber 506 exerts a force on thearmature 502 andvalve member 504, returning them to their initial position. Fluid from theouter feedback chamber 506 exits through an exhaust port (not shown). The fluid path is indicated by arrows. The fluid travels between thecylindrical nozzle body 508 andrectangular piston base 510. It then travels under thepiston base 510 and through a hole in thewasher 512. -
FIG. 6 shows a cross-sectional view of the solenoid fluid control valve taken at the dashedline 514 inFIG. 5 . As illustrated by the arrows inFIG. 6 , fluid travels from an inner to an outer area between the washer and the bobbin and exits through anexhaust port 600. The departure of fluid from the outer feedback chamber reduces the pressure in that area, allowing the spool to return to its initial position. - Returning to
FIG. 3 , the dual gain solenoidfluid control valve 300 requires less force from thecoil 306 than the direct acting solenoid fluid control valve ofFIG. 1 requires. The force from thecoil 306 is only required to displace thevalve member 314 from the opening in 318 in thepiston 316. Once thevalve member 314 is displaced, fluid in theinner feedback chamber outer feedback chamber 350 provides the force that displaces thespool 220 and compresses thespring mechanism 242. - In contrast, the force from the
coil 106 in the direct acting solenoidfluid control valve 100 shown inFIG. 1 must be sufficient to displace theentire spool 112 and compress thespring mechanism 122. This greater force requires more turns of thecoil 106, resulting in a larger, more expensive device. The dual gain solenoid fluid control valve utilizes the fluid pressure in the inner and outer feedback chambers to move the spool, thereby requiring fewer turns of the coil, and therefore allowing for a reduction in the device's size and cost. - The dual gain solenoid fluid control valve has a further advantage of improved robustness to contamination. Contamination can greatly affect the performance of a solenoid fluid control valve, as small contaminants in the fluid flowing through the valve may become lodged between moving and stationary elements, obstructing the smooth motion of the armature and spool. This obstruction may lead to hysteresis, as well as to variable responses to a given command current. Accordingly, the presence of contaminants may quickly degrade the solenoid fluid control valve's performance and reliability.
- The first and second feedback chambers of the dual gain solenoid fluid control valve allow fluid to travel through wide passages within the device. The fluid may carry contaminants, but the wide chambers allow the valve to function without being inhibited by the contaminants. This increased robustness improves the reliability of the device, allowing for look-up tables to be created relating a current in the coil for a resulting control pressure. The lifetime of the device may also be extended as wear due to contaminants is minimized.
- While the dual gain solenoid fluid control valve may be used as an on/off switch for the control pressure, a pulse width modulated (PWM) signal may be used to provide variations in the control pressure. The spring cap may be tightened or loosened to adjust the position of the spool in the energized and de-energized states. Once the two positions have been determined, the duty cycle of the PWM signal may determine how much time the solenoid spends in each state, thereby creating a variable control pressure.
- Another embodiment of the dual gain solenoid fluid control valve is shown in
FIGS. 7 and 8 , wherein like numbers as inFIGS. 2 and 3 indicate like elements. Referring toFIG. 7 , the dual gain solenoidfluid control valve 700 is in the de-energized state. In this embodiment, the radial spool bore 744 is moved to a tapered region of thespool 720. In the de-energized state, the radial spool bore 744 is open to thesupply port 724 and thecontrol port 732. - Referring to
FIG. 8 , when thecoil 806 is energized, the dual feedback from theinner feedback chamber outer feedback chambers 850 moves the spool such that the radial spool bore 844 is open to thesupply port 832 and theexhaust port 838. However, as in the first embodiment of the dual gain solenoid fluid control valve, thecalibration cap 840 may be tightened or loosened to adjust the force of thespring mechanism 842 on thespool 820. This force in turn determines the position of thespool 820 when thecoil 806 is in the de-energized and energized states. Accordingly, the spool position in the de-energized and energized states may not exactly correspond to the positions shown inFIGS. 7 and 8 . - Referring to
FIG. 8 , the inner and outer feedback pressure now depends on both the supply and control pressures, and not just the supply pressure. Further, the placement of the radial spool bore 844 allows the device to be configured such that a small control pressure remains even when thecoil 806 is energized, and the control pressure it at a minimum. Having a non-zero minimum control pressure allows the valve to be more responsive to a change in the current through the coil. This improved response allows the valve to be more accurately controlled by a PWM signal. - The dual gain solenoid fluid control valve may be used to control a variable displacement pump, wherein the valve's control pressure regulates the flow of fluid through the pump. The pump requires that the valve's response to a given command current be accurate and reliable, so that the command current may be correlated with a flow through the pump. The dual gain solenoid fluid control valve provides a reliable control pressure that is robust to contamination and responsive to small changes in the command current.
Claims (20)
Priority Applications (7)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US14/206,442 US9404599B2 (en) | 2014-03-12 | 2014-03-12 | Dual/variable gain oil pump control valve |
ES14720010.9T ES2661119T3 (en) | 2014-03-12 | 2014-03-18 | Oil pump control valve with double / variable gain |
EP14720010.9A EP3117131B1 (en) | 2014-03-12 | 2014-03-18 | Dual/variable gain oil pump control valve |
KR1020167027938A KR101921400B1 (en) | 2014-03-12 | 2014-03-18 | Dual/variable gain oil pump control valve |
CA2942531A CA2942531C (en) | 2014-03-12 | 2014-03-18 | Dual/variable gain oil pump control valve |
CN201480077106.XA CN106104126B (en) | 2014-03-12 | 2014-03-18 | Solenoid control valve for fluids |
PCT/US2014/031051 WO2015137984A1 (en) | 2014-03-12 | 2014-03-18 | Dual/variable gain oil pump control valve |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
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US14/206,442 US9404599B2 (en) | 2014-03-12 | 2014-03-12 | Dual/variable gain oil pump control valve |
Publications (2)
Publication Number | Publication Date |
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US20150260302A1 true US20150260302A1 (en) | 2015-09-17 |
US9404599B2 US9404599B2 (en) | 2016-08-02 |
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US14/206,442 Expired - Fee Related US9404599B2 (en) | 2014-03-12 | 2014-03-12 | Dual/variable gain oil pump control valve |
Country Status (7)
Country | Link |
---|---|
US (1) | US9404599B2 (en) |
EP (1) | EP3117131B1 (en) |
KR (1) | KR101921400B1 (en) |
CN (1) | CN106104126B (en) |
CA (1) | CA2942531C (en) |
ES (1) | ES2661119T3 (en) |
WO (1) | WO2015137984A1 (en) |
Cited By (12)
Publication number | Priority date | Publication date | Assignee | Title |
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US20160319947A1 (en) * | 2013-12-20 | 2016-11-03 | Gea Farm Technologies Gmbh | Safety valve |
US20180073649A1 (en) * | 2016-09-12 | 2018-03-15 | Thomas Magnete Gmbh | Seat Valve With Electromagnetic Actuation |
JP2019007579A (en) * | 2017-06-27 | 2019-01-17 | 株式会社ケーヒン | Hydraulic control device |
US10426128B2 (en) | 2013-12-20 | 2019-10-01 | Gea Farm Technologies Gmbh | Safety valve device |
JP2019173875A (en) * | 2018-03-28 | 2019-10-10 | Kyb株式会社 | Solenoid proportional control valve |
US10499610B2 (en) | 2008-06-27 | 2019-12-10 | Gea Farm Technologies, Inc. | Milk tube dome with flow controller |
US10527176B2 (en) | 2016-09-12 | 2020-01-07 | Thomas Magnete Gmbh | Seat valve with electromagnetic actuation |
US10681895B2 (en) | 2010-02-22 | 2020-06-16 | Gea Farm Technologies, Inc. | Dairy animal milking preparation system and methods |
US10874084B2 (en) | 2004-06-12 | 2020-12-29 | Gea Farm Technologies, Inc. | Safety valve for a dairy system component |
US11015722B2 (en) | 2016-05-04 | 2021-05-25 | Gea Farm Technologies Gmbh | Safety valve |
US11206805B2 (en) | 2017-11-03 | 2021-12-28 | Gea Farm Technologies Gmbh | Automated milking system safety valve arrangement |
US11723341B2 (en) | 2009-09-04 | 2023-08-15 | Gea Farm Technologies, Inc. | Safety valve for an automated milker unit backflushing and teat dip applicator system |
Families Citing this family (5)
Publication number | Priority date | Publication date | Assignee | Title |
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CA3038969A1 (en) | 2016-12-30 | 2018-07-05 | Parker-Hannifin Corporation | Valve with gradual flow area changes |
JP2019039541A (en) * | 2017-08-29 | 2019-03-14 | 日本電産トーソク株式会社 | Hydraulic control device |
JP2019039542A (en) * | 2017-08-29 | 2019-03-14 | 日本電産トーソク株式会社 | Hydraulic control device |
US10302201B2 (en) | 2017-08-30 | 2019-05-28 | Sun Hydraulics, Llc | Enhancement of valve flow and pressure characteristics in valves and hydraulic systems |
US11248717B2 (en) | 2019-06-28 | 2022-02-15 | Automatic Switch Company | Modular smart solenoid valve |
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- 2014-03-12 US US14/206,442 patent/US9404599B2/en not_active Expired - Fee Related
- 2014-03-18 EP EP14720010.9A patent/EP3117131B1/en not_active Not-in-force
- 2014-03-18 CA CA2942531A patent/CA2942531C/en active Active
- 2014-03-18 KR KR1020167027938A patent/KR101921400B1/en active Active
- 2014-03-18 WO PCT/US2014/031051 patent/WO2015137984A1/en active Application Filing
- 2014-03-18 CN CN201480077106.XA patent/CN106104126B/en not_active Expired - Fee Related
- 2014-03-18 ES ES14720010.9T patent/ES2661119T3/en active Active
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US3722547A (en) * | 1970-10-21 | 1973-03-27 | Schneider Co Optische Werke | Pilot valve |
US3824898A (en) * | 1972-04-12 | 1974-07-23 | R Pauliukonis | Energy conserving directional valve-cylinder combination |
US3736958A (en) * | 1972-04-13 | 1973-06-05 | Lockheed Aircraft Corp | Four-way solenoid selector valve |
US4245671A (en) * | 1976-08-26 | 1981-01-20 | Shoketsu Kinzoku Kogyo Kabushiki Kaisha | Solenoid pilot operated valve |
US4199942A (en) * | 1978-09-28 | 1980-04-29 | Eaton Corporation | Load sensing control for hydraulic system |
US4538643A (en) * | 1982-06-11 | 1985-09-03 | Kienzle Apparate Gmbh | Electropneumatic pilot control stage for a pneumatic servo valve |
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Cited By (20)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US11540484B2 (en) | 2004-06-12 | 2023-01-03 | Gea Farm Technologies, Inc. | Safety valve for a dairy system component |
US10874084B2 (en) | 2004-06-12 | 2020-12-29 | Gea Farm Technologies, Inc. | Safety valve for a dairy system component |
US10499610B2 (en) | 2008-06-27 | 2019-12-10 | Gea Farm Technologies, Inc. | Milk tube dome with flow controller |
US12096743B2 (en) | 2009-09-04 | 2024-09-24 | Gea Farm Technologies, Inc. | Safety valve for a dairy system component |
US11723341B2 (en) | 2009-09-04 | 2023-08-15 | Gea Farm Technologies, Inc. | Safety valve for an automated milker unit backflushing and teat dip applicator system |
US10681895B2 (en) | 2010-02-22 | 2020-06-16 | Gea Farm Technologies, Inc. | Dairy animal milking preparation system and methods |
US11627718B2 (en) | 2010-02-22 | 2023-04-18 | Gea Farm Technologies, Inc. | Dairy animal milking preparation system and methods |
US10426128B2 (en) | 2013-12-20 | 2019-10-01 | Gea Farm Technologies Gmbh | Safety valve device |
US10502330B2 (en) * | 2013-12-20 | 2019-12-10 | Gea Farm Technologies Gmbh | Safety valve |
US20160319947A1 (en) * | 2013-12-20 | 2016-11-03 | Gea Farm Technologies Gmbh | Safety valve |
US11015722B2 (en) | 2016-05-04 | 2021-05-25 | Gea Farm Technologies Gmbh | Safety valve |
US10527176B2 (en) | 2016-09-12 | 2020-01-07 | Thomas Magnete Gmbh | Seat valve with electromagnetic actuation |
US10393280B2 (en) * | 2016-09-12 | 2019-08-27 | Thomas Magnete Gmbh | Seat valve with electromagnetic actuation |
US20180073649A1 (en) * | 2016-09-12 | 2018-03-15 | Thomas Magnete Gmbh | Seat Valve With Electromagnetic Actuation |
JP2019007579A (en) * | 2017-06-27 | 2019-01-17 | 株式会社ケーヒン | Hydraulic control device |
US11617343B2 (en) | 2017-11-03 | 2023-04-04 | Gea Farm Technologies Gmbh | Automated teat dip fluid manifold |
US11206805B2 (en) | 2017-11-03 | 2021-12-28 | Gea Farm Technologies Gmbh | Automated milking system safety valve arrangement |
US11930782B2 (en) | 2017-11-03 | 2024-03-19 | Gea Farm Technologies Gmbh | Automated milking system safety valve arrangement |
JP7007970B2 (en) | 2018-03-28 | 2022-01-25 | Kyb株式会社 | Electromagnetic proportional control valve |
JP2019173875A (en) * | 2018-03-28 | 2019-10-10 | Kyb株式会社 | Solenoid proportional control valve |
Also Published As
Publication number | Publication date |
---|---|
CA2942531A1 (en) | 2015-09-17 |
KR20160130492A (en) | 2016-11-11 |
KR101921400B1 (en) | 2019-02-13 |
EP3117131A1 (en) | 2017-01-18 |
ES2661119T3 (en) | 2018-03-27 |
CN106104126B (en) | 2018-10-19 |
US9404599B2 (en) | 2016-08-02 |
WO2015137984A1 (en) | 2015-09-17 |
CA2942531C (en) | 2019-02-19 |
EP3117131B1 (en) | 2018-01-17 |
CN106104126A (en) | 2016-11-09 |
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